Liquid pump



K. SCHOENE LIQUID PUMP Filed May 20, 1937 2 Sheets-Sheet l Snnentor XM/7k baloana Gttornegs Sept. 6, 1938.

Sept. 6, 1938.

K. SCHOENE 2,129,073V

LIQUID PUMP Filed May 20, 1957 2 Sheets-Sheet 2 :inventor ALW@ am Gttomegs Patented Sept. 6, 1938 UNITED STATES PATENT OFFICE LIQUID PUMP Kurt Schoene, Hamburg, Germany Application May 20, 1937, Serial No. 143,836 In Germany June 15, 1936 5 Claims.

'Ihis invention relates to liquid pumps of the reciprocating plunger type, and resides in features permitting the use of relatively high suction and discharge heads in `pumps operating at high speeds.

In a prior patent, No. 2,033,852, issued March 10, 1936, I disclose and claim a reciprocating pump in which a single sleeve valve encircling the cylinder, controls both theinlet and discharge ports which are separated from each other by means of a partition forming a sealed joint with the single sleeve valve. This prior patent also shows automatic or suction operated inlet valves which are designed to operate in the initial portion of the suction stroke before the sleeve valve fully opens the inlet port. the function of the automatic valve being to permit the pump to operate successfully at high speeds and relatively high suction head.

The present invention involvesifeatures of improvement upon the pump shown in my prior patent above identified. If the structure of the prior patent be used in pumping against a high discharge head the valve operating .gear is subjected to a considerable unbalanced force because the upper end of the valve sleeve is subject to discharge pressure and the lower end is subject to suction pressure. Thus 'thepermissible discharge head in the device of the prior patent is limited by the permissible unbalanced load upon the valve gear.

One feature of the present invention involves the substitution for a single sleeve valve of two distinct sleeve valves, one controlling suction and the other vcontrolling discharge. Each sleeve valve is balanced and the two are connected together to operate in unison by means of rods which pass through packing glands in the partition which separates the suction anddischarge passages. Consequently, the unbalanced hydraulic pressures affect merely the areas of these connecting rods, the sleeve valves themselves being balanced as to the hydraulic pressures which react upon them.

Another feature of the present invention is an arrangement whereby the inlet sleeve valve, when in its open position, closes the ports leading to the automatic inlet valves, or at least throttles these ports, the effect in either case being to accelerate the closing of the automatic inlet valves. This accelerated closing permits successful operation at somewhat higher speeds.

In the accompanying drawings I show several embodiments of the inventionindicating that the (Cl. 10S- 227) featuresA above described may be successfully used singly or in combination with each other.

In the drawings- Fig. 1 is an axial section through the working space of a. single-acting plunger pump embodying the features of invention above described. lThe plunger is shown in full lines at mid-stroke in the suction stroke with the valve mechanism in the corresponding position. The head end and crank end dead point positions of the plunger are each indicated in dotted lines.

Fig. 2 is a similar view showing a modification in which automatic discharge valves are used instead of a sleeve discharge valve.

Fig. 3 is a similar view of a modification in which the inlet sleeve valve does not control the automatic inlet valve ports.

' In the above figures the actuating mechanism for the plunger and the valve ,is not indicated, for the reason that it is conventional and follows generally the arrangement used in connection with my prior patent above identified. Ordinarily the plunger would be reciprocated by a crank, and the valve sleeves would be actuated by eccentrics or cranks angularly displaced from the `plunger operating crank by substantially Thus when the plunger is at mid-stroke, the valve sleeve is at one or the other limit of its motion, and vice versa. Actuating mechanisms of this type are standard in the art.

Referring first to Fig. 1, 5 represents a housing which together with the partition I9 forming a part thereof, defines a suction passage 6 which encircles the working space of the pump and a separate discharge passage 'l which also encircles the upper portion of the working space of the pump. Pressed intoI the housing 5 is a cylinder liner or bushing 8 in which the pump plunger 9 reciprocates. The plunger 9 makes `a close sliding fit in the liner 8 and may be provided with packing means, though none is indicated in the drawings and none is strictly necessary. Formed in the upper end of the liner 8 are a series of auxiliary inlet ports H which lead from the suction passage 6 to the working space above the plunger 9 and are controlled by automatic valve means here conventionally represented as a simple ring valve l2.

Seating on the upper end ofthe liner 8, and sealing therewith, is a combined head and grid port structure comprising the head element proper i3, an annulus I4, and a second annulus l5, all connected together by a series of plate-like radial vanes I6. The annulus l5, whose form is clearly indicated in the drawings, encircles the upper end of the liner 8 and seats thereagainst. The annulus I4 separates the main inlet ports I'I from the discharge ports I8. The inlet passages 6 are separated from the discharge passages 'I by the annular partition I9, above mentioned, and this p artition I9 is sealed to the annulus I4 by means 0f an annular filler piece 2 I.

The above construction is adopted to facilitate assembly. The structure provides aworking space having at its upper end an annular series of grid discharge ports I8 and below these an annular series of grid inlet ports I'I. The grid ports I8 are controlled by an annular sleeve valve 22, the controlling edge of which is the lower edge. 'I'he grid ports I1 are controlled by an annular sleeve valve 23, the upper edge of which is the controlling edge. The sleeve valves 22 and 23 are connected together by rods 24 which pass through stufng boxes 25 in the annular member 2|.

It will be observed that the inlet and discharge ports open in alternation witheach other and that when the inlet port is fully open, or substantially so, as indicated in Fig. 1, the sleeve valve 23 closes the auxiliary inlet ports I I. While I prefer complete closure of the ports II, partial closure accelerates the closing movement of the automatic valve I2 and therefore attains a useful result.

The valves 22 and 23 are reciprocated by valve rods 26 which are actuated in harmony with each other by eccentrics on the crank shaft.

The two sleeve valves shown in Fig. l are what might be described as of the inside cut-off type,

that is, the controlling edges of the two sleeve valves 22 and 23 are the proximate edges. This arrangement is essential if the sleeve valve 23 is to control the auxiliary inlet ports II.

If this last feature is not desired, then the construction shown in Fig. 3 can be used. In this figure, the structure is similar to that described with reference to Fig. 1 and similar parts are identified by the reference numerals used in Fig. 1, differentiated by the letter a..

In Fig. 3, the upper or outer edge of the sleeve valve 22a is the controlling edge and the lower or outside edge of the sleeve valve 23a is the controlling edge. In other words, the sleeve valves are of the outside cut-off type. It follows that during the operation of the pump, motion of the sleeve valves in Fig. 3 is the reverse of the motion of the sleeve valves in Fig. 1. When the sleeve inlet valve of Fig. 3 is fully opened, no throttling of the auxiliary inlet ports IIa occurs. In fact these ports are never throttled by the sleeve valve 23a.

The structure illustrated in Fig. 3 has the advantage secured by using separateinlet and discharge sleeve valves but lacks the advantage secured by controlling the auxiliary inlet ports by the inlet sleeve valve. It is also inferior to the structure shown in Fig. 2 because the structure is necessarily higher, a very important point under certain conditions of installation.

In Fig. 2 a modified construction is shown in which automatic discharge valves of the ring type are substituted for the sleeve discharge valve shown in Fig. 1, but the sleeve inlet valve conforms to the arrangement shown in Fig. 1. In Fig. 2 a housing 5b defines the inlet passage 6b and the discharge passage 1b, the two being separated by an annular partition I9b. A liner 8b, similar to the liner 8, receives a reciprocating plunger 9b. There are auxiliary inlet ports IIb controlled by an automatic inlet valve I2b. The head structure I3b is formed with annular ports controlled by automatic ring discharge valves, conventionally indicated Vat 21. Formed integrally with the head structure I3b are the radial vanes I 6b which terminate in an annulus I5b similar in form and function to the annulus I5 of Fig. 1. There are grid inlet ports I1b which are controlled by a sleeve inlet valve 23D, which also controls the auxiliary inlet portsv IIb. The inlet valve is actuated by valve rods 2Gb, similar to the valve rods 26 of Fig. 1.

The structure shown in Fig. 2 permits an arrangement which is even lower and more compact than that shown in Fig. 1, the advantage arising from the fact that the upper edge of the valve 23b is the controlling edge, so that the valve moves downward from the main inlet ports into the space occupied by the auxiliary inlet ports. The automatic discharge valve `mechanism takes even less space than the sleeve discharge mechanism of Fig. 1 because it is unnecessary to provide lateral ports.

The feature of eliminating or minimizing the unbalanced pressure in the sleeve valve permits the use of the pump herein disclosed, with high discharge heads, while the feature of throttling the auxiliary inlet ports permits the use of higher speeds at high suction heads. As pointed out this last arrangement permits a reduction of overall height. Combination of the various features indicated in Fig. 1 allows the use of a high speed reciprocating pump with suction and discharge heads, each of which is high, and produces a very compact mechanism.

In the drawings, the construction has been simplied as much as possible in order to emphasize the principles of the invention, and it is to be understood that refinements of design well known in the art, may be resorted towithout departing from the spirit of the invention. For example, while the automatic valves illustrated are of elemental simplicity, there is nothing in the invention which precludes the use of highly rened types of valve such as are well known in the art, and nothing to preclude the use of valve closing springs where their use is considered desirable. The use of such springs is not, however, a feature of the present invention, and therefore not illustrated.

What is claimed is:

1. In a liquid pump of the expansible chamber type, the combination of means forming a working space having spaced main inlet and discharge ports and an auxiliary inlet port.; reciprocating liquid-displacing means for varying the volume of said working space; a reciprocable balance sleeve valve encircling said working space and controlling said discharge port; a reciprocable balanced sleeve valve encircling said working space and controlling said main inlet port, said valve serving to close said auxiliary inlet port at least partially when the main inlet port is fully open; a suction operated valve also controlling said auxiliary inlet port; and means connecting said sleeve valves to move in unison in such manner as to open the discharge and main inlet ports in alternation, said connecting means being substantially unaffected by the differential between suction and discharge pressures.

2. In a liquid pump of the expansible chamber type, the combination of means forming a working space having spaced inlets and discharge ports; reciprocating liquid-displacing means for varying the volume of said working space; a reciprocable balanced sleeve valve encircling said working space and controlling said discharge port; reciprocable balanced sleeve valve encircling said working space and controlling said inlet port; and means connecting said sleeve valves to move in unison in such manner as to open vsaid discharge and inlet ports in alternation, said connecting means being substantially unaffected by the differential between inlet and discharge pressures. l

3. In a liquid pump of the expansible chamber type, the combination of means forming a work space having spaced main inlet and discharge ports and an auxiliary inlet port; reciprocating liquid-displacing means f or varying the volume ofsaid working space; a reciprocabl balanced sleeve valve encircling said working space and controlling said discharge port; a reclprocable balanced sleeve valve encircling said working space and controlling said main port; a suction operated valve controlling said auxiliary inlet port; and means connecting said sleeve valves to move in unison in such manner as to open said discharge and main inlet ports in alternation, said connecting means being substantially unaffected by the differential between inlet and discharge pressures.

4. In a liquid pump of the expansible chamber type, the combination of means forming a working space having spaced main inlet and discharge ports and an auxiliary inlet port; reciprocating liquid-displacing means for varying the volume of said working space; valve means controlling said discharge port; a reciprocable balanced sleeve valve encircling said Working space andcontrol- 'ling said main inlet port, said valve serving to close said auxiliary inlet port at least partially when the main inlet port is fully open; a suction operated valve also controlling said auxiliary inlet port; and means substantially unaffected by the dilerential between inlet and discharge pressures for driving the discharge valve means from said balanced valve.

5. In a liquid pump of the expansible chamber type, the combination of means forming a working space having a discharge port and two series of peripheral inlet ports, one series being main inlet ports and the other being auxiliary inlet ports; valve means controlling the discharge ports; automatic valve means controlling said auxiliary inlet ports; and a balanced sleeve valve reciprocable to close said main-and auxiliary inlet ports in alternation, whereby the space occupied by the series of auxiliary ports is availed of to accommodate `motion of the sleeve valve, and the required space for the inlet valve mechanism is minimized. f

` KURT SCHOENE. 

